JPH05172199A - Planetary transmission assembly - Google Patents

Abstract

(57) [Abstract] [Purpose] A planetary transmission assembly that outputs five forward gear ratios and one reverse gear ratio using six torque transmission devices. [Structure] Each planetary gear set 34, 46 is a sun gear 3
2, 44, ring gears 56, 50, and a plurality of pinions 48, 52, 54, and the pinions are supported by a common carrier 40. At least two of the six torque transmission devices 26 are input clutch members 28 for selectively connecting the input means 14 to predetermined elements of the planetary gear set, and at least two other are reaction brake members for selectively fixing predetermined elements of the planetary gear set. 38. The sun gear 44 of one planetary gear set is connected to at least one of the input clutch members, and the sun gear 32 of the other planetary gear set is at least one of the input clutch members and one of the reaction brake members.
Connected to one. The carrier is connected to one of the input clutch members and one of the reaction brake members, and the ring gear 50 of one planetary gear set is connected to the output shaft 18.

Description

Detailed Description of the Invention

[0001]

FIELD OF THE INVENTION This invention relates to automatic transmissions or transmissions. More specifically, the present invention provides that a pair of compound planetary gear sets selectively actuates one or several of a plurality of torque transmitting (transferring) devices having an input clutch member and a reaction brake member. A planetary transmission assembly that provides a forward speed ratio (gear ratio) and a reverse speed ratio (gear ratio). In particular, the present invention includes a pair of planetary gear sets that are interlocked by a series of pinions that engage each other and also selected sun and ring gears within individual planetary gear sets of a compound planetary transmission. A composite planetary transmission assembly adapted to be connected.

The present invention is particularly suitable for use in vehicles.
Related to high speed automatic transmission (transmission). That is, the transmission provides five forward speed ratios or gear ratios and one reverse speed ratio or gear ratio. To simplify the following description, the forward gear ratio is defined as a gear ratio that moves the vehicle forward.For simplification, the structure of the planetary gear set is such that the output member is the input member at the forward gear ratio. Suppose it rotates in the same direction as. Conversely, the reverse gear ratio causes the vehicle to move backwards, in which case the output member is assumed to rotate in the opposite direction of the input member.

[0003]

2. Description of the Related Art As is well known, an input member receives a driving force, that is, a driving torque from a vehicle engine through a known torque converter and provides the driving torque to a planetary gear set which constitutes a planetary transmission (usually). , In the form of a shaft in the transmission) is a connection mechanism. The known output member is also a connecting mechanism (usually in the form of a shaft) that connects the transmission to a differential for rotating the drive wheels.

"Torque transmitting device" is another term commonly used in the description of planetary gear sets. Two types of torque transmission devices are generally known. That is, the input clutch member and the reaction brake member. The input clutch member is typically used to interconnect the two relatively rotatable members so as to rotate the two members together. The reaction brake member is selectively used to prevent rotation of the rotatably mounted member. The reaction brake member is provided by the housing that houses the transmission, and thus the reaction brake member typically secures a rotatable member to the housing to prevent it from rotating.

Most known automatic transmissions required more than one planetary gear set to achieve a five-step forward ratio or gear ratio as provided in the transmission of the present invention.

A typical planetary gear set has a sun gear composed of a small gear located in the center of the planetary gear set, and a ring gear as an outermost member that defines the outer boundary of the planetary gear set and has inward facing teeth. A plurality of planet gears, or pinions, are located between the sun gear and the ring gear, and rotate (spin) or revolve. The pinion in each planetary gear set is usually supported by a carrier, and when the pinion revolves, the carrier rotates in response to the revolving motion. Alternatively, the carrier may rotate to produce the desired movement of the pinion. When the sun gear is rotated, all the elements in the planetary gear set except the sun gear are driven unless one of the elements is held stationary by a torque transmitting device, such as a reaction brake member provided from the transmission housing. When the reaction brake member locks one of the elements in the planetary gear set to the housing, the fixed element is held in place and all other elements move relative to this fixed element. By selectively locking the elements of the planetary gearset and selectively connecting the input shaft to the desired elements of the planetary gearset, typical means are provided for providing different gear ratios from the planetary gearset. That is, different members to be rotated or fixed are selected in order to appropriately change the speed and direction of the output to meet the current conditions.

[0007]

However, there is a limit to the number of changes that a single planetary gear set can provide. As a result, multiple planetary gear sets have been compounded to provide a greater number of speed ratios or gear ratios. The combination of planetary gear sets results in selective interconnection between members of the individual planetary gear sets, as well as one of the planetary gear sets.
Various torque transmission devices are used to secure the above elements to the transmission housing. While such an arrangement (such as that disclosed in U.S. Pat. No. 4,802,385) is effective, it provides a planetary gear set and the torque transmission necessary to provide the desired number of gear ratios. It increases the length of the housing needed to house it.

A unique construction that provides the desired combination for a pair of planetary gear sets is US Pat.
No. 719. In this configuration, a pair of planetary gear sets are combined by using a unique pinion community. The arrangement disclosed in this U.S. patent provides four forward gear ratios by selectively actuating five torque transmitting devices. However, this configuration cannot provide a five-step forward gear ratio.

Therefore, it is an object of the present invention to provide an improved five speed transmission by combining two planetary gear sets.

Another object of the present invention is to provide a five-speed transmission of the type described above which can be easily incorporated into a housing having an overall size smaller than conventional overall sizes.

Yet another object of the present invention is to use a pair of planetary gear sets combined by the interaction of pinions supported on a common carrier, the pinions interacting with each other and the sun and ring gears of the two planetary gear sets. To provide a five-speed transmission of the type described above which is also made to interact with it.

Another object of the present invention is to provide a five speed transmission of the type described above in which a compound planetary gear set is driven by selectively actuating six torque transmitting devices.

Yet another object of the present invention is that the six torque transmitting devices have at least two input clutch members and at least two reaction braking members of the above type.
To provide a fast transmission.

[0014]

SUMMARY OF THE INVENTION A planetary transmission assembly according to the present invention is a planetary transmission assembly that provides five forward gear ratios and one reverse gear ratio, a transmission housing and an input. Means; output means; a pair of axially spaced sun gears rotationally mounted in the transmission housing; and a pair of axially spaced ring gears rotationally mounted in the transmission housing,
A ring gear, one of which is fixed to the output means; a carrier that is rotatably mounted in the transmission housing; a carrier that can rotate independently of the carrier, and that rotates or revolves with the carrier when the carrier rotates. A plurality of pinions supported by the carrier for movement and at least six torque transmission devices (26) such as clutches and brakes, the pinions being grouped in at least pairs, A planetary transmission assembly in which grouped pinions are in mesh, at least one pinion is engaged for each sun gear, and at least one pinion is engaged for each ring gear. To achieve the purpose, each ring gear is axially aligned with the corresponding sun gear. A torque transmission device comprising means (48, 160, 162) including at least one pinion for directly engaging one of the sun gears with a ring gear axially spaced from the sun gear; For selectively connecting said input means to at least one of said sun gear and said carrier
It is characterized by having one input clutch member (28) and also having at least two reaction braking members (38) for selectively fixing at least the carrier and one of the sun gears to the transmission housing.

The present invention has at least two input clutch members connected between the input member and the output member and connected to the sun gear and the planet carrier, and at least two brake members connected to the sun gear and the planet carrier. A composite planetary gear set controlled by at least six torque transmission devices, the planetary gear set having a ring gear continuously connected to the output member, the other ring gear and the other sun gear, and the other ring gear and the other sun gear. A multi-speed power transmission can be provided, each connected to a torque transmitting device.

A planetary transmission assembly embodying the principles of the present invention uses a pair of planetary gear sets housed within a common transmission housing. Each planetary gear set has a sun gear and a ring gear. A plurality of pinions are supported on a common carrier. The sun and ring gears of the two planetary gear sets are interengaged by actuating a pinion provided by a common carrier.

Six torque transmitting devices are used within the planetary transmission assembly. At least two of the torque transmitting devices are in the form of input clutch members that are selectively used to provide a drive connection between the relatively rotatable elements of the two planetary gear sets. At least the other two are in the form of reaction braking members that are selectively used to prevent rotation of selected rotatable elements in the planetary gear set by locking them to the transmission housing. is doing.

The input shaft is adapted to be selectively connectable to the elements of the compound planetary gear set via an input clutch member. In particular, the sun gear in one planetary gear set can be selectively connected to at least the input shaft, and the sun gear in the other planetary gear set can be selectively connected to the input shaft as well as being fixed via one of the reaction brake members. It is also possible to be done. Also, the carrier can be selectively connected to the input shaft and can be secured via one of the reaction brake members.
The ring gear in one planetary gear set is connected to the output shaft.

[0019]

DETAILED DESCRIPTION OF THE PREFERRED EMBODIMENT FIG. 1 shows at 10 an embodiment of an epicyclic transmission assembly or planetary transmission assembly embodying the present invention. As is well known, the planetary transmission assembly 10 receives input from an engine 12 connected to an input shaft 14 via a torque converter 16. As is also well known, the output shaft 18 extends outwardly from the planetary transmission assembly 10 and connects through a differential mechanism 20 to a vehicle's left drive shaft 22A and right drive shaft 22B with wheels 24 attached.

The input shaft 14 of the planetary transmission assembly 10 cooperates with a plurality of torque transfer devices 26 in the form of input clutch members 28.

In the following detailed description, particular components, elements or arrays may be used in one or more positions. Common reference numerals are used to refer generally to this type of component, element or array, but wherever a particular single component, element or array is individually identified, these are generally referred to. The reference numbers used for reference will be indicated with the subscripts hidden. Thus, throughout the specification and drawings, for example, a plurality of input clutch members are generally identified by the reference numeral 28, although specific individual input clutch members are designated as input clutch members 28A, 28B, 2
It will be specified as 8C. Also, the convention for this subscript is used throughout the specification.

Referring to FIG. 1, the input shaft 14 is rotatably (in a possible state) connected to a sun shaft 30 via an input clutch member 28A. The sun shaft 30 transmits the input torque to the sun gear 32 of the first planetary gear set 34. The sun shaft 30 is also fixed to a transmission housing 36 in which a planetary transmission assembly 10 is surrounded by a torque transmission device 26 in the form of a reaction brake member 38A. When the reaction brake member 38A is actuated, the sun gear 32 also becomes a reaction member.

The input shaft 14 is the input shaft 1.
The carrier 40 can be rotated by an input clutch member 28B that selectively connects 4 to the carrier shaft 42. Similarly, the input shaft 14 is connected to the second sun gear 47 by the input clutch member 28C that connects the input shaft 14 to the second sun gear 47.
4 can be rotated.

With the above structure, the drive torque from the input shaft 14 is transmitted through the sun gear 32 or 44 or the carrier 40, and the planetary transmission assembly 1 is then transmitted.
Obviously, it is introduced into the zero planetary gear set 34, 46.

The planetary gear sets 34, 46 are incorporated into the compound gear structure by the pinion from the carrier 40 as follows. That is, the first planetary gear set 3
The sun gear 32 in 4 is directly meshed with the long pinion 48 which is directly meshed with the ring gear 50 in the second planetary gear set 46. The long pinion 48 also has two short pinions 5.
It meshes with 2, 54. The short pinion 52 meshes with the ring gear 56 in the first planetary gear set 34, and the short pinion 54 meshes with the sun gear 44 in the second planetary gear set 46. Long pinion 48 and short pinion 52, 5
All 4 are mounted on a carrier 40 so that they can rotate individually, and when any pinion revolves in the circumferential direction, the carrier 40 rotates. Second planetary gear set 4
The ring gear 50 in 6 is simply an element in the planetary transmission assembly 10 that connects directly to the output shaft 18. Therefore, the long pinion 48 must rotate (orbit) or revolve to produce the output from the planetary transmission assembly 10 (FIG. 1).

In the embodiment shown in FIG. 1, two additional reaction braking members are provided. In particular, the ring gear 56 in the first planetary gear set 34 is
8B can be selectively fixed to the transmission housing 36, and the carrier 40 is a reaction brake member 38C.
Can be fixed to the transmission housing 36.

The planetary transmission assembly 10 of FIG.
Selectively activates or engages the six torque transmitting devices 26, that is, the three input clutch members 28.
A, 28B, 28C and three reaction brake members 38
A, 38B, and 38C are controlled to provide a desired five forward gear ratio (speed ratio). Also, in the embodiment shown in FIG. 1, the carrier 40 is used during normal operation.
There is also provided a one-way torque transmission mechanism 58 used to establish the as a reaction member. During the shift period between the first gear ratio and the second gear ratio, the one-way torque transmission mechanism 58 provides a smooth shift and accurate timing. The reason is that only one friction torque transmission drive interchange is required to complete this shift. This is a well known means utilized to provide smooth transmission operation. A procedure table is shown in FIG. 2 in order to facilitate understanding of the procedure (sequence) of the torque transmission device 26 for obtaining a desired series of gear ratios. These torque transmission devices 26 (input clutch member 2
8 or reaction brake member 38), each gear ratio (1
Items that need to be operated in order to obtain the forward gear ratio and the reverse gear ratio from the fifth speed to the fifth speed are indicated by x in the table. Therefore, for this embodiment, reference is made to the table of FIG. 2 as well as the detailed description below to determine the torque transmitting device 26 that must be actuated to obtain each gear ratio. FIG. 2 also exemplarily shows the torque ratio for each gear ratio so that it can be better understood to some extent for a typical installation. However, it goes without saying that the number of gear teeth and the diameters of the various elements in the planetary gear set influence the specific torque ratio obtained in such a transmission.

The first gear ratio or highest gear ratio (lowest speed output) is established by engaging the input clutch member 28C. As a result, the second planetary gear set 4
A drive connection is created between the second sun shaft 47, which drives the sun gear 44 in 6, and the input shaft 14. The one-way torque transfer mechanism 58 prevents reverse rotation of the carrier 40, thereby establishing the carrier 40 as a reaction member. Instead, if you need engine braking,
Reaction brake member 38C is engaged to establish carrier 40 as a reaction member. in this way,
For this gear ratio, the sun gear 44 is the input element of the planetary transmission assembly 10.

Assuming that the sun gear 44 rotates clockwise, the short pinion 54 in the second planetary gear set 46 rotates counterclockwise, which forces the long pinion 48 to rotate clockwise. When the long pinion 48 rotates clockwise, the output ring gear 50 follows this rotation and rotates itself clockwise against the resistance between the wheels 24 and the road surface. As a result, the vehicle makes a forward motion at low speed (and thus at the maximum torque that can be supplied by the output shaft 18).

The second forward gear ratio is achieved by engaging the reaction brake member 38A to establish the sun gear 32 as a reaction member and rotating the carrier 40 forward, thereby disengaging the one-way torque transmission mechanism 58. Is obtained by When the reaction brake member 38C is engaged, the reaction brake member 38 is operated by an ordinary control mechanism.
Simultaneous interchange of C and 38A occurs. The purpose of the one-way torque transmission mechanism 58 is to provide a means for maintaining a torque load on the transmission that facilitates a smooth transition during the shift from the first gear ratio to the second gear ratio. The one-way torque transmission mechanism 58 produces this effect by preventing reverse rotation of the carrier 40. As is known, this effect can be provided by a variety of different control means, including electronic shift mechanisms. The present invention utilizes a one-way brake for simplicity of operation,
It does not exclude the possibility of other means for achieving the same or substantially similar effects.

As a result of the above operating procedure, at first gear ratio, the sun gear 44 constitutes the input element of the planetary transmission assembly 10. Reaction brake member 3
When 8A is activated, the sun gear 32 is fixed to the transmission housing 36, and
The rotation of the sun gear 32 becomes a reaction element of the planetary gear set 34. In the first speed gear ratio, the input shaft 14 is connected via the input clutch member 28C.
The sun gear 44 connected to is continuously rotating clockwise. This clockwise rotation of the sun gear 44 drives the short pinion 54 counterclockwise and rotates the long pinion 48 clockwise. This rotation of the long pinion 48 causes the long pinion 48 to revolve around the sun gear 32. The reason is that the sun gear 32 is stationary because it is fixed to the transmission housing 36 by the reaction brake member 38A. Due to the above-described revolution movement and rotation (rotation) movement, the ring gear 50 rotates clockwise at a speed higher than the first gear ratio, and this rotation is carried to the wheels 24 by the output shaft 18, and the first gear is applied by applying low torque. Produces a faster output speed than the ratio.

The forward gear ratio of the third speed is the reaction brake member 3
It is obtained by releasing the engagement of 8A and engaging the input clutch member 28B. The input clutch member 28B remains engaged. In this configuration, the sun gear 44 and the carrier 40 rotate clockwise at the same speed. Carrier 40
This rotation causes the long pinion 48 to revolve clockwise, thereby rotating the ring gear 40 clockwise and transmitting the input torque to the output shaft 18. Since the sun gear 44 and the carrier 40 rotate at the same speed, the short pinion 52 and the long pinion 48 do not rotate about their own axes but merely revolve around the circumference. Therefore, the ring gear 50 rotates in the same direction at the same speed as the sun gear 44 and the carrier 40, and produces an output in the same direction at the same speed as supplying the same torque as the input shaft 14. A torque ratio and speed of 1.00 is generally known as direct drive, and the third forward gear of the present invention is the direct drive gear.

The forward gear ratio of the fourth speed is determined by the input clutch member 2
This is obtained by maintaining the input clutch member 28B in the engaged state while releasing the engagement of 8C and keeping the reaction brake member 38A engaged. As a result of this change, the sun gear 32 is held stationary by the reaction brake member 38A and the carrier 40 rotates clockwise at the same speed as the input shaft 14. As a result, the long pinion 48 acting on the stationary sun gear 32 rotates right about its own axis. The ring gear 50 that directly meshes with the long pinion 48 is rotated clockwise in response to the clockwise rotation of the long pinion 48. Since all force transmission elements of the transmission rotate in the same direction, the speed transmitted from the sun gear 32 to the long pinion 48 and then to the ring gear 50 is increased. However, the torque decreases proportionally. Thus, at this 4th gear ratio, the rotational directions of the input and output members are maintained in the same direction to provide the forward gear ratio, but the output speed is increased above that of the 3rd forward gear ratio. Since the 3rd forward gear ratio is direct drive (equal input speed and output speed), this 4th gear ratio provides an overdrive condition (output speed greater than input speed). In this case, the torque output is proportional to the input torque, but smaller than the input torque. The fifth forward gear ratio is obtained by maintaining the input clutch member 28B in the engaged state with the reaction brake member 38A released and the reaction brake member 38B engaged. By maintaining the engagement of the input clutch member 28B, the carrier 40 maintains the input member in the fourth gear ratio. When the reaction brake member 38B operates, the ring gear 56 becomes a reaction member. When the carrier 40 rotates clockwise, the long pinion 48 revolves clockwise and the short pinion 52 rolls around the stationary ring gear 56. Therefore, the long pinion 48 meshing with the short pinion 52 is rotated clockwise while revolving. Therefore, the ring gear 50 receives an input from the long pinion 48 which rotates and revolves clockwise. As a result, the ring gear 50 rapidly rotates to the right, giving the output shaft 18 a corresponding rotation. Thus, the 5th gear ratio provides a faster output than the 4th gear ratio at the same input speed.
However, the torque ratio becomes smaller accordingly. This fifth gear ratio actually provides the second overdrive condition.

The reverse gear ratio is obtained by disengaging all torque transmitting devices and then simultaneously engaging reaction brake member 38C and input clutch member 28A. Disengaging all input clutch members and reaction members results in what is known as the neutral position,
In this neutral position, the engine is operating but produces no output from the transmission. In the neutral state, the reverse gear ratio is provided by the engagement of the two torque transmission devices described in detail later.

In particular, the engagement of the input clutch member 28A causes the sun gear 32 to rotate clockwise with the input shaft 14. When the reaction brake member 38C is engaged, the carrier 40 is fixed and this carrier becomes the reaction member. Therefore, the long pinion 48 meshing with the sun gear 32 is rotated counterclockwise. The ring gear 50 meshing with the long pinion 48 is driven counterclockwise by the long pinion 48. As a result, the input shaft 1
A left rotation of the output shaft 18 opposite the right rotation of 4 occurs, thereby providing a reverse gear ratio. With this reverse gear ratio, the speed ratio is small, but the torque ratio is correspondingly large.

Another embodiment of a planetary transmission assembly embodying the principles of the present invention is shown at 110 in FIG.
As is known, the planet transmission assembly 110 receives input via an input shaft 114 within the planet transmission assembly 110. Also, as is commonly known, the output shaft 118 extends outwardly from the planetary transmission assembly 110 and is connected via a differential mechanism 120 to a vehicle's left drive shaft 122A and right drive shaft 122B with wheels 124 mounted thereto. To do.

The input shaft 114 of the planetary transmission assembly 110 cooperates with a plurality of torque transfer devices 126 in the form of input clutch members 128.

Referring to FIG. 3, the input shaft 114 is connected to the sun shaft 130 via an input clutch member 128A.
Is connected (in a ready state) to. Sun shaft 1
Reference numeral 30 designates the second planetary gear set 1 in this embodiment.
The input torque is transmitted to the sun gear 132 incorporated in 46. The sun shaft 130 is also fixed to the transmission housing 136 in which a torque transmission device 126 in the form of a reaction brake member 38A surrounds the planetary transmission assembly 110. The reaction brake member 138A is used which makes the sun gear 132 a reaction member when the reaction brake member 138A is actuated.

The input shaft 114 can rotate the carrier 140 by an input clutch member 128B that selectively connects the input shaft 114 to the carrier shaft 142. Similarly, the input shaft 114
In this embodiment, the sun gear 144 of the first planetary gear set 134 can be rotated. The sun shaft 147 attached to the sun gear 144 is the input clutch member 128.
When selectively connected to the input shaft 114 by C, the sun gear 144 rotates.

With the above construction, as in the embodiment of FIG.
The drive torque from the input shaft 114 is the sun gear 13
2 or 144, or via the carrier 140, the planetary gear set 1 of the planetary transmission assembly 110.
34, 146.

The planetary gear sets 134, 146 are combined by the pinion from the carrier 140 as follows. That is, the first long pinion 160 is connected to the sun gear 132 and the ring gear 1 in the second planetary gear set 146.
It is arranged between 50 and and these are simultaneously engaged. Similarly, the second long pinion 162 is connected to the first planetary gear set 1
It is arranged between the sun gear 144 and the ring gear 156 in the gear 34 and meshes with them at the same time. In addition, the long pinions 160, 162 mesh together.

The two long pinions 160, 162 are rotatably mounted on the carrier 140, and when the long pinion orbits in the circumferential direction, the carrier 14 is rotated.
When 0 rotates and vice versa, the long pinion revolves. The ring gear 150 in the second planetary gear set 146 is just one element in the planetary transmission assembly 110 that connects directly to the output shaft 118. Therefore, the long pinions 160, 162 are shown in FIG.
Must rotate or revolve to produce the output from the planetary transmission assembly 110 shown in FIG.

In the embodiment shown in FIG. 3, two additional reaction braking members are provided. In particular, the ring gear 156 in the first planetary gear set 134 is coupled to the transmission housing 136 by the reaction brake member 138B.
The carrier 140 can be selectively fixed to the transmission housing 13 by the reaction brake member 138C.
Can be fixed to 6.

The planetary transmission assembly 11 of FIG.
0 by selectively using the six torque transmitting devices 126, namely, the three input clutch members 128A,
128B, 128C with three reaction brake members 138
Various combinations of A, 138B, 138C are controlled to provide the desired five forward gear ratios.

Although the structure of this embodiment is different from that of the first embodiment, the function and operating means are almost the same. In particular, in this embodiment, the first gear ratio is obtained by engaging the input clutch member 128C and the reaction brake member 138C. The torque supplied by the input shaft 114 is transmitted to the sun gear 144 by the sun shaft 147, which causes the sun gear to rotate right in response to the right rotation of the input shaft 114. When the reaction brake member 138C is actuated to lock the carrier 140, the carrier becomes a reaction member, thereby preventing the long pinions 160, 162 from revolving. However, in response to the right rotation of the sun gear 144, the long pinion 1
62 rotates counterclockwise, forcibly rotating the pinion 160 clockwise. This rotation of the pinion 160 is the ring gear 1
A right rotation of 50 is produced, providing torque to the output shaft 118, which causes the output shaft 118 to rotate in the same direction at a slower speed than the input shaft 114.

The second forward gear ratio disengages the reaction brake member 138C and causes the reaction brake member 1 to disengage.
Input clutch member 128C with 38A engaged
Is maintained by maintaining the engagement. As a result, the sun gear 144 remains the input element of the planetary transmission assembly 110, and clockwise rotation of the sun gear 144 causes the long pinion 162 to rotate counterclockwise. Due to this rotation of the long pinion 162, the long pinion 160
Is forced to rotate clockwise, and when this rotation occurs,
With the reaction brake member 138A engaged, the sun gear 1
Since the 32 and the sun shaft 130 are held stationary, the two long pinions 160, 162 revolve. When the long pinions 160 and 162 perform the revolving motion described above, the carrier 140 rotates clockwise and the ring gear 1
Give 50 a right turn. The rotation of the output ring gear 150 is slightly faster than the output of the first gear ratio because of the long rotational movement and the revolution movement of the pinion 160. The torque output is proportional to the torque output of the first embodiment, but smaller than that.

3 for planetary transmission assembly 110
To obtain a fast forward gear ratio, the input clutch member 12
The reaction brake member 138A while maintaining the engagement of 8C.
Is disengaged and the input clutch member 128B is engaged. Engagement of the input clutch members 128B and 128C forces the carrier shaft 142 and the sun shaft 147 to rotate clockwise at the same speed. The reason is that both of these shafts are directly connected to the input shaft 114. As a result, the sun gear 14
4 and the carrier 140 rotate in the same direction at the same speed. As is well known, when two elements of a planetary gear set rotate at the same speed, the other elements must also rotate at that speed. Therefore, the ring gear 150 and the output shaft 118
Also rotates at that speed. This is known as a direct drive ratio (direct drive ratio), and the input / output speed, the input / output torque, and the rotation direction thereof are the same.

The forward gear ratio of the fourth speed is determined by the input clutch member 1
It is obtained by maintaining the input clutch member 128B in the engaged state with the engagement of 28C disengaged and the reaction brake member 138A still engaged. Here, when the reaction brake member 138A is operated, the sun gear 13
2 is fixed and cannot rotate. Input clutch member 1
Activating 28B causes carrier 140 to rotate clockwise in response to clockwise rotation of input shaft 114. This rotation of the carrier 140 causes the long pinion 160 to roll clockwise around the stationary sun gear 132, causing the carrier 1
The ring gear 150 is rotated clockwise at a rotation speed higher than 40. Therefore, the fourth speed drive gear ratio constitutes an overdrive ratio, in which case the ring gear 150 rotates faster than the input shaft 114, but the torque supply is even smaller.

The 5th forward gear ratio is equivalent to that of the reaction brake member 1.
This is obtained by maintaining the input clutch member 128B in the engaged state with the engagement of 38A disengaged and the reaction brake member 138B engaged. This gear ratio, like the two gear ratios described above, utilizes the carrier 140 as an input element for the planetary transmission assembly 110. 5
The high gear ratio utilizes the ring gear 156 as a reaction member. The carrier 140 provides a clockwise input, forcing the long pinion 162 to rotate counterclockwise within the fixed ring gear 156. When the long pinion 162 rotates counterclockwise, the long pinion 160 rotates clockwise, thereby driving the ring gear 150 clockwise. This 5
The high gear ratio provides a second overdrive condition in which ring gear 150 rotates at a faster speed than input shaft 114, but at a lower output torque.

In planetary transmission assembly 110, all input clutch members and all reaction brake members are disengaged and then input clutch member 128A is engaged with reaction brake member 138C to provide a reverse gear ratio. Is obtained. Engagement of input clutch member 128A causes sun shaft 130, and thus sun gear 132, to rotate clockwise in response to clockwise rotation of input shaft 114. Reaction brake member 13
When the 8C is actuated, it locks the carrier 140 to prevent it from rotating, which causes the long pinions 160, 16 to rotate.
It prevents the translational movement of the two, but forces them to rotate about their own axis. Therefore, the clockwise rotation of the sun gear 132 forcibly rotates the long pinion 160 counterclockwise. This left rotation of the long pinion 160 causes the ring gear 15 to rotate.
0 is forced to rotate counterclockwise. This allows
Ring gear 150 rotates in the opposite direction to input shaft 114 (thus providing a reverse gear ratio) with greater torque than that provided by input shaft 114.

A second alternative embodiment of a planetary transmission assembly embodying the principles of the present invention is shown at 210 in FIG. As is well known, the planetary transmission assembly 2
10 receives input via an input shaft 214 within the planetary transmission assembly 210. Also, as is commonly known, the output shaft 218 extends outwardly from the planetary transmission assembly 210 and has a left drive shaft 222A of the vehicle with wheels 224 mounted through a differential mechanism 220.
And to the right drive shaft 222B.

The input shaft 214 of the planetary transmission assembly 210 cooperates with a plurality of torque transfer devices 226 in the form of input clutch members 228.

Referring to FIG. 4, the input shaft 214 is connected to the sun shaft 230 via an input clutch member 228A.
Is connected (in a ready state) to. Sun shaft 2
Reference numeral 30 denotes the second planetary gear set 2 in this embodiment.
The input torque is transmitted to the sun gear 232 incorporated in 46. The sun shaft 230 is also fixed to a transmission housing 236, within which a torque transmission device 226 in the form of a reaction brake member 238A surrounds the planetary transmission assembly 210. Similar to the previous embodiments, the reaction brake member 238A is used to make the sun gear 232 the reaction member when the reaction brake member 238A is actuated.

The input shaft 214 can also rotate the carrier 240 by an input clutch member 228B that selectively connects the input shaft 214 to the carrier shaft 242.

With the above structure, the driving torque from the input shaft 214 is controlled by the sun gear 232 or the carrier 240.
Is introduced into the planetary gear set 246 of the planetary transmission assembly 210 via.

The planetary gear sets 234 and 246 are combined by the pinion from the carrier 240 as follows. That is, the first long pinion 260 is connected to the sun gear 232 and the ring gear 2 in the second planetary gear set 246.
It is arranged between 50 and and these are simultaneously engaged. Similarly, the second long pinion 262 is connected to the first planetary gear set 2
It is arranged between the sun gear 244 and the ring gear 256 in the gear 34, and meshes with them at the same time. Additionally, the long pinions 260, 262 are mated together.

The two long pinions 260, 262 are mounted rotatably together on the carrier 240 so that when the long pinion translates circumferentially, the carrier 24
When 0 rotates and vice versa, the long pinion translates. Also, the second planetary gear set 2
Note that ring gear 250 in 46 is only one element in planetary transmission assembly 210 that connects directly to output shaft 218. Accordingly, the long pinions 260, 262 must rotate or translate to produce the output from the planetary transmission assembly 210 shown in FIG.

In the embodiment shown in FIG. 4, three additional torque transmission devices in the form of reaction braking members are provided. In particular, the ring gear 256 in the first planetary gear set 234 can be selectively fixed to the transmission housing 236 by the reaction brake member 238B, and the carrier 240 can be fixed to the transmission housing 236 by the reaction brake member 238C.
4 can be fixed to the transmission housing 236 by a reaction brake member 238D.

The planetary transmission assembly 21 of FIG.
0 has only two input clutch members 228A, 228B, but a total of six torque transmission devices (the rest four reaction brake members 238A, 238B, 238C,
238D). Various combinations of these torque transmission devices can provide the desired five forward gear ratios described below.

The operation of this embodiment is in many ways the same as the operation of the previous two embodiments, but there are certain differences. Figure 4
In this embodiment, the first forward gear ratio is obtained by actuating the input clutch member 228A and the reaction brake member 238D. Assuming that the input shaft 214 is rotating clockwise as in the previous embodiments, this rotation causes the sun shaft 230 to rotate through the operating input clutch member 228B, causing the sun gear 232 to rotate clockwise. Rotate to. The clockwise rotation of the sun gear 232 causes the meshed long pinion 260 to be forcedly rotated counterclockwise. Actuating reaction brake member 238D to secure sun gear 244 causes long pinion 262 to translate clockwise around sun gear 244. The combined rotational and translational motion of the long pinions 260, 262 drives the ring gear 250 clockwise, which in turn
The output shaft 218 is rotated in the same direction as the input shaft 214 at a lower speed and a larger torque.

The forward gear ratio of the second speed is determined by the input clutch member 2
28A by disengaging and engaging the input clutch member 228B. Reaction brake member 23
8D maintains the state where the sun gear 244 is fixed to the transmission housing 236, and the input clutch member 2
When 28B is actuated, carrier 240 rotates clockwise with input shaft 214. The clockwise rotation of the carrier 240 causes the long pinions 260, 262 to translate clockwise. Since the sun gear 244 is fixed, the clockwise translational movement of the long pinion 262 is
Rotate 2 left about its own axis even during its clockwise translation. The clockwise translational and counterclockwise rotational movements of this combination of long pinions allow the ring gear 250 to rotate at a speed faster than that provided by the first forward gear ratio, but slower than the rotational speeds of the carrier 240 and the input shaft 214. Rotate clockwise.

The third forward gear ratio is obtained by disengaging the reaction brake member 238D and engaging the input clutch member 228A. As a result, the input clutch members 228A and 228B are engaged with each other, and the sun gear 2
Rotate 32 and carrier 240 in the same direction and at the same speed. As is well known, when two elements of a planetary gear set rotate at the same speed, the other elements must also rotate at that speed. Therefore, the ring gear 250 and the output shaft 218 also rotate in the same direction as the input shaft 214 at the same speed. Therefore, the third forward gear ratio is a direct drive ratio.

The forward gear ratio of the fourth speed is determined by the input clutch member 2
28A is disengaged and reaction brake member 238A is engaged. The input clutch member 228B remains activated so that the carrier 240 constitutes the input element. Here, the reaction brake member 238
When A is operated, the sun gear 232 is fixed. As a result, the carrier 240 rotates clockwise in response to clockwise rotation of the input shaft 214, forcing the long pinion 260 to rotate clockwise around the fixed sun gear 232.
In this mode of operation, the ring gear 250 is forced to rotate clockwise with the rotational and translational speeds of the long pinion 260 combination. Therefore, the ring gear 250
The output shaft 218 is rotated in the same rotation direction as the input shaft 214 and at a speed higher than the input shaft speed. Therefore, the fourth forward gear ratio is the first overdrive ratio provided by the embodiment of FIG.

The 5th forward gear ratio is equivalent to that of the reaction brake member 2
38A by disengaging and actuating reaction brake member 238B. Input clutch member 228B remains activated to maintain carrier 240 as an input member at this gear ratio. The reaction brake member 238B fixes the ring gear 256.
Therefore, clockwise rotation of the carrier 240 with the input shaft 214 results in clockwise translation of the long pinions 260,262. Since the long pinion 262 meshes with the fixed ring gear 256, the translational motion of the long pinion 262 causes the pinion to rotate counterclockwise. This counterclockwise rotation of the long pinion 262 causes the long pinion 260 meshed with it to rotate clockwise. The combined rotational and translational motion of the long pinion 260 causes a faster rotation of the ring gear 250 in the same direction as the input shaft 214, providing a second overdrive condition.

The reverse gear ratio is obtained by first disengaging the previously actuated torque transmitting device 226 and then engaging the input clutch member 228A with the reaction brake member 238C. When the input clutch member 228A is actuated, the sun gear 23 together with the input shaft 214 is activated.
2 rotates clockwise. When the reaction brake member 238C is actuated, the carrier 240 is fixed, which causes
The pinion 260 in which the clockwise rotation of the sun gear 232 is long is rotated counterclockwise. Pinion 2 with long ring gear 250
Being driven by 60, the ring gear 250 rotates counterclockwise, providing counter rotation of the output shaft 218 at a slower speed but with a relatively large torque.

A third alternative embodiment of a planetary transmission assembly embodying the principles of the present invention is shown at 310 in FIG. As is well known, the planetary transmission assembly 3
10 receives input via an input shaft 314 within the planetary transmission assembly 310. Also, as is commonly known, the output shaft 318 extends outwardly from the planetary transmission assembly 310 and has a left drive shaft 322A of the vehicle with wheels 324 mounted through a differential mechanism 320.
And the right drive shaft 322B.

The input shaft 314 of the planetary transmission assembly 310 cooperates with a plurality of torque transfer devices 326 in the form of input clutch members 328.

Referring to FIG. 5, the input shaft 314 is connected to the sun shaft 330 via the input clutch member 328A.
Is connected (in a ready state) to. Sun shaft 3
Reference numeral 30 designates the second planetary gear set 3 in this embodiment.
The input torque is transmitted to the sun gear 332 incorporated in 46. The sun shaft 330 is also fixed to a transmission housing 336, within which housing a torque transmission device 326 in the form of a reaction brake member 338A surrounds the planetary transmission assembly 310. Similar to the previous embodiments, the reaction brake member 338A is used to make the sun gear 332 the reaction member when the reaction brake member 338A is actuated.

The input shaft 314 can also rotate the carrier 340 by an input clutch member 328B that selectively connects the input shaft 314 to the carrier shaft 342.

With the above structure, the driving torque from the input shaft 314 is controlled by the sun gear 332 or the carrier 340.
Via a planetary gear set 334 and / or 346 of the planetary transmission assembly 310. The planetary gear sets 334, 346 are combined by the pinion from the common carrier 340 as follows. That is, the first long pinion 360 is connected to the sun gear 332 and the ring gear 35 in the second planetary gear set 346.
It is arranged between 0 and 0 and meshes with them at the same time. Similarly, the second long pinion 362 is connected to the first planetary gear set 3
It is arranged between the sun gear 344 and the ring gear 356 in the gear 34, and meshes with them at the same time. In addition, the long pinions 360,362 mesh together.

The two long pinions 360 and 362 are rotatably mounted on the carrier 340, and when the long pinion is translated in the circumferential direction, the carrier 34 is rotated.
When 0 rotates and vice versa, the long pinion translates. Also, the second planetary gear set 3
Note that the ring gear 350 in 46 is simply one element in the planetary transmission assembly 310 that connects directly to the output shaft 318. Therefore, the long pinions 360, 362 must rotate or translate to produce the output from the planetary transmission assembly 310 shown in FIG.

In the embodiment shown in FIG. 5, one additional reaction brake member is provided. In particular, the carrier 34
Zero can be selectively fixed to the transmission housing 336 by the reaction brake member 338B. This embodiment also has two additional input clutch members 328. In particular, the input clutch member 328C selectively connects the input shaft 314 to the sun gear 344 of the first planetary gear set 334 via the sun shaft 347, and the input clutch member 328D selectively connects the ring gear 356 to the input shaft 314.

The planetary transmission assembly 31 of FIG.
0 has only two reaction brake members 338A, 338B, but a total of six torque transmission devices (the rest are 4
Input clutch members 328A, 328B, 328C,
328D). Various combinations of these torque transmission devices can provide the desired five forward gear ratios described below.

In order to obtain the first forward gear ratio in the third alternative embodiment of FIG. 5, the input clutch member 328C and the reaction brake member 338B are actuated. When the input clutch member 328C is actuated, the input shaft 314
Along with that, the sun gear 344 rotates clockwise. Due to this rotation of the sun gear 332, a long pinion 362 that meshes
Is rotated counterclockwise. However, the carrier 340
Is fixed by the reaction brake member 338B, thus preventing translational movement of the long pinion 362. Therefore, the counterclockwise rotation of the long pinion 362 causes the long pinion 360 to rotate clockwise, which causes the ring gear 3 to rotate.
Via 50, output shaft 318 is rotated clockwise at a slower speed and greater torque than input shaft 314.

The second forward gear ratio is obtained by disengaging the reaction brake member 338B and engaging the reaction brake member 338A. Input clutch member 3
28C continues to provide drive input to sun gear 344,
At this time, the carrier 340 rotates freely. When the reaction brake member 338A is operated, the sun gear 332 is fixed. When the sun gear 344 rotates clockwise in response to the clockwise rotation of the input shaft 314, the meshed long pinion 362 rotates counterclockwise, causing the long pinion 360 to rotate clockwise. Since the sun gear 332 is fixed, clockwise rotation of the long pinion 360 causes clockwise translational motion of the long pinion 360. Long pinion 3
This clockwise rotation of 60 drives ring gear 350 clockwise and causes output shaft 318 to rotate clockwise. The output shaft 318 rotates in the same direction as the input shaft 314 at a speed slightly faster than that provided by the first forward gear ratio, and with less torque.

The third forward gear ratio is obtained by disengaging the reaction brake member 338A and actuating the input clutch member 328B. The previously operated input clutch member 328C continues to operate, and the sun gear 34
4 and the input clutch member 328B provides carrier 340 with the same rotational speed. As a result, Sun Gear 3
44 and carrier 340 rotate in the same direction and at the same speed. As mentioned above, when two elements of a planetary gear set rotate at the same speed, the other elements must also rotate at that speed. Therefore, under the condition of the third forward gear ratio,
The ring gear 350 includes a sun gear 344 and a carrier 340.
Rotates clockwise at the same speed as. Therefore, the output shaft 318 rotates in the same direction as the input shaft 314 and at the same speed, and therefore the third forward gear ratio is the direct drive ratio.

The forward gear ratio of the fourth speed is determined by the input clutch member 3
28C is disengaged and reaction brake member 338A is engaged. Input clutch member 3
28B remains engaged and continues to rotate carrier 340 clockwise in response to clockwise rotation of input shaft 314. The reaction brake member 338A is operated to fix the sun gear 332. As a result of fixing the sun gear 332,
The rotation of the carrier 340 forces the pinion 360, which has a long rotation, to rotate clockwise. Therefore, ring gear 350 is subject to a combination of clockwise rotation and translational speed of long pinion 360. This causes the ring gear 350 to rotate the output shaft 318 at a faster speed than the speed of the input shaft 314. This fourth forward gear ratio is the first overdrive ratio provided by the embodiment of FIG.

The fifth forward gear ratio in this embodiment is obtained by disengaging the input clutch member 328B and engaging the input clutch member 328D. Therefore, the ring gear 356 serves as an input member. The reaction brake member 338A is maintained in operation, and the sun gear 332 is operated as a reaction member.

Since the sun gear 332 is fixed, when the carrier 340 rotates clockwise, the long pinion 36
Zero rotates clockwise as it rolls around the fixed sun gear 332. This clockwise rotation of long pinion 360 causes long pinion 362 meshing with ring gear 356 to rotate counterclockwise. Therefore, the long pinion 36
In order to give the longer pinion 362 the required counterclockwise rotation, the carrier 340 needs to be rotated clockwise at a faster rate. Rotation of the carrier 340 by rotation of the long pinion 360 resulting from the driving force of the ring gear 356 when causing the reaction of the long pinion 360 with the fixed sun gear 332 causes additional translation of the long pinion 360 required to rotate the carrier 340. Combined with the movement, it allows rotation of the long pinion 362 relative to the ring gear 356. The resulting rotation of the long pinions 360, 362 is fixed by the fixed sun gear 3.
Required by 32. The above-described actuation of the input clutch member 328D, in combination with the actuation of the reaction brake member 338A, causes the ring gear 350 to rotate at a relatively high rate of clockwise rotation, causing a second overdrive condition for the planetary transmission assembly 310. provide.

To obtain the reverse gear ratio, the previously engaged torque transmission device 326 is disengaged and the input clutch member 328A and the reaction brake member 338B are simultaneously engaged. When the input clutch member 328A is actuated, the sun gear 332 rotates clockwise and the long pinion 3
Rotate 62 counterclockwise. Reaction brake member 338
When B is actuated, carrier 340 is locked, which prevents translational movement of long pinion 362 and causes left rotation of ring gear 350. Therefore, the output shaft 318 rotates with a relatively large torque in the direction opposite to the input shaft 314.

From the above description of the above embodiments,
One ring gear 50, 150, 250, 350 always serves as an output member, and one sun gear 32, 132, 23
2, 332 and carriers 40, 140, 240, 340
Are each always connected to a pair of selectively engageable torque transmission devices (one is an input clutch member and the other is a reaction brake member). Each of the remaining planet members, the other sun gear, and the ring gear is always connected to a selectively engageable torque transmission device (which may be an input clutch member or a reaction brake member). Accordingly, a wide range of design choices are available that allow the planetary transmission assembly to meet specific requirements and installation requirements.

Although the use of the one-way torque transmission mechanism has been described for only the embodiment of FIG. 1, such a mechanism for controlling the carrier as a reaction member at a low speed ratio can be used for other embodiments. Therefore, in a planetary transmission assembly, two, three or four clutches and four, three or two brakes may be used in combination to provide a total of six torque transmitting devices. This is a control element for providing at least five stages of forward speed ratio and at least one reverse speed ratio by a composite structure using a ring gear as an output member and a sun gear and a carrier as an input / reaction member. It is the minimum number of torque transmission devices.

[Brief description of drawings]

FIG. 1 has two planetary gear sets combined with one specific pinion structure and six to achieve the desired gear ratio.
1 is a schematic configuration diagram of a planetary transmission assembly according to an embodiment of the present invention, which also incorporates two selectively engageable torque transmission devices.

FIG. 2 is a table showing the operating conditions of the torque transmission device necessary to provide the five forward gear ratios and one reverse gear ratio available from the transmission shown schematically in FIG.

FIG. 3 is a schematic configuration diagram of a planetary transmission assembly according to a first alternative embodiment of the present invention.

FIG. 4 is a schematic configuration diagram of a planetary transmission assembly according to a second alternative embodiment of the present invention.

FIG. 5 is a schematic configuration diagram of a planetary transmission assembly according to a third alternative embodiment of the present invention.

[Explanation of symbols]

10, 110, 210, 310 Planetary transmission assembly 14, 214, 314 Input shaft 16 Torque converter 18, 218, 318 Output shaft 26 Torque transmission device 28, 228, 328 Input clutch member 32, 44, 132, 144, 232, 332, 344
Sun gear 34, 46, 134, 146 Planetary gear set 36 Transmission housing 38, 238, 338 Reaction brake member 40 Carrier 48, 52, 54, 160, 162 Pinion 50, 56, 150, 156, 256, 356 Ring gear

 ─────────────────────────────────────────────────── ─── Continued Front Page (72) Inventor John Dee Malloy, Michigan, USA 48098, Troy, Dublin Fair 6877

Claims (7)

[Claims] 1. A planetary transmission assembly providing five forward gear ratios and one reverse gear ratio, comprising:
A transmission housing (36); an input means (14, 16); an output means (18); a pair of axially spaced sun gears (32, 44) rotatably mounted in the transmission housing; A pair of axially separated ring gears (50, 56) that are rotatably mounted on the
0) a ring gear fixed to the output means; a carrier (40) rotatably mounted in the transmission housing; and a carrier capable of rotating independently of the carrier, and together with the carrier when the carrier rotates. A plurality of pinions (48, 52, 54) supported by the carrier so as to be able to rotate or revolve, and a torque transmission device (26) such as at least six clutches and brakes; and at least the pinion. Grouped as a pair, the grouped pinions mesh, each sun gear has at least one pinion engaged, and each ring gear has at least one pinion engaged. In the planetary transmission assembly, each of the sun gears and shafts to which each of the ring gears corresponds is Directionally aligned and surrounding; means (48, 1) including at least one pinion for directly engaging one of the sun gears with a ring gear axially spaced from the sun gear.
60, 162); said torque transmitting device having at least two input clutch members (28) for selectively connecting said input means to at least one of said sun gear and said carrier, and at least said carrier and Planetary transmission assembly, also comprising at least two reaction brake members (38) for selectively securing one of said sun gears to said transmission housing. 2. The six torque transmitting devices include three input clutch members (28) and three reaction brake members (3).
8) and; each sun gear (32, 44) is selectively connectable to the input means (14) via the input clutch member; the output means (18)
The planetary transmission assembly of claim 1, wherein said ring gear (56) not connected to is selectively secured to said transmission housing (36) via one of said reaction braking members. 3. The six torque transmitting devices have four input clutch members (328) and two reaction braking members (338); each of the sun gears (332, 34).
4) the input means (3) via the input clutch member.
14) so that the ring gear (356), which is not connected to the output means (318), can be selectively connected to the input means via one of the input clutch members. The planetary transmission assembly of claim 1, wherein the planetary transmission assembly is fixed. 4. The six torque transmitting devices have two input clutch members (228) and four reaction brake members (238); one of the sun gears (232) is through the input clutch members. The input means (214)
Is selectively connected to the ring gear (2) which is not connected to the output means (218).
The planetary transmission assembly of claim 1, wherein (56) is selectively secured to said transmission housing via one of said reaction braking members. 5. The sun gears (32, 44) and the ring gears (56, 50) surrounding them form a planetary gear set (34, 46), and the pinion (48, 52, 54). Interconnects the sun gear and the ring gear of each planetary gear set; the planetary transmission assembly comprises two planetary gear sets, wherein the planetary gear set comprises two planetary gear sets. 6. The sun gear (32) of at least a first pinion (48) of one planetary gear set (34) and the ring gear (5) of the other planetary gear set (36).
0); at least a second pinion (54) engages the first pinion and the other sun gear (44); at least a third pinion (52) engages the first pinion and the other. The planetary transmission assembly of claim 5, wherein said planetary gear assembly engages said ring gear (56) of said. 7. The sun gear (13) of at least one first pinion (160) of one planetary gear set (146).
2) and the ring gear (150); at least a second pinion (162) engages the sun gear (144) and the ring gear (156) of the other planetary gear set (134); The planetary transmission assembly of claim 5, wherein the second pinions are interconnected.